Governor apparatus



Aug. 6, 1935. w ENGEL 2,009,995

GOVERNOR APPARATUS v Filed July 5, 1934 '4 Sheets-Sheet 2 3 WI! flnyel 6! Wbaflalle 0. B fleiber 1935- w. F. 'ENGEL El AL 2,009,995

GOVERNOR APPARATUS Filed July 3, 1934 '4 SheetsSheet s wucwtou 3 WI. En el 0. B Treiber Summp Q 4;, anmais alle Aug. 6,-1935. w. F, ENGEL'EI' AL v2,009,995

GOVERNOR APPARATUS Filed July 5, 1934] 4 Sheets-Sheet 4 I wowntou WI. r1961 6 W'flab'alle 0. B Trezjber Patented Aug, 6, 1935 UNITED STATES common mm'rus Williaml.Engel,GeorgeW.La8alle,and0tis D. 'lreiber, Canton, Ohio, alsignors to Hercules Motors Corporation, Canton, Ohio, a corporation of Ohio Application Jilly 3, 1984, Serial No. 133,630

15 Chilly (Cl. 284-3) The invention relates in general to governor apparatus adapted for association with means controlling the speed of rotation of a shaft, whereby regardless of the setting of the control 5 means the maximum speed of rotation of the shaft is maintained at a predetermined limit, and whereby a particular or idling speed of rotation of the shaft may be maintained automatically,

More particularly the invention relates to governor apparatus of the foregoing general character which is adapted for use in connection with a compression ignition internal combustion engine utilizing preferably liquid "hydrocarbon fuel such as Diesel 011, and used as the motive power for a vehicle such as a truck, bus, commercial car, passenger car, or the like.

From another standpoint, the invention relates to governor apparatus of the foregoing general character and which in one form'is adapted for use in connection with a compression ignition internal combustion engine utilizing preferably liquid hydrocarbon fuel such as diesel oil and used as a variable torque controlled source of power for a power shovel, in which an increase in torque is desirable with increasing engine speeds up to a predeterminedintermediate engine speed which may be 900 R. P. M., after which the torque automatically falls oil at a predetermined rate with a further increase in the engine speed to a second intermediate engine speed, which may be 1300 R. P. M, and after which the torque very rapidly falls oil with further overrunning or increase in speed of the engine to the maximum speed.

Governor apparatus of the foregoing type for the control of vehicle motive power, have included relative complex mechanisms, which have been relatively diflicult to adjust both with respect to the maximum speed governor action and the idling speed governor action. I

Governor apparatus of the foregoing type and adapted for variable torque control have not been heretofore generally available. I

The objects of the present improvements include in general the provision of such governor apparatus in which the construction and arrangement of the parts of the governor apparatus is simplified so as to facilitate the manufacture and maintenance of the same.

Further objects of the present improvements include the provision of governor apparatus of the foregoing description, and which includes simplified adjusting means for setting the apparatus with respect to the governor action both at the idling and maximum speeds, such adjusting means being externally accessible.

Further objects of the present improvements include the provision of governor apparatus of the foregoing description which includes sim- 5 giglled and improved means for stopping the en- Further objects of the present improvements include the provision of governor apparatus of the foregoing description, one form of which is 10 adapted for providing variable automatic torque control for a compression ignition internal combustion engine used as a source of power for a power shovel and the like.

Further objects of the present improvements 15 include the provision of governor apparatus of the foregoing description, and the construction and arrangement of which is such as to permit interchangeable use of certain of the parts in the present improved apparatus or in the improved 20 governor apparatus set forth in the prior application for U. 8. Letters Patent of George W. La

Salle, Serial No. 694,434, the apparatus of said by the improvements, apparatus, parts, combinations and sub-combinations, which comprise the present invention, and the nature of which is set forth in the following general statement, and preferred embodiments of which, together with their mode of use are set forth in the following description, and which are particularly and distinctly pointed out and set forthin the 40- appended claims forming part hereof.

The nature of the present invention may be described in general terms as including a rotary shaft, power drive means for the shaft, variable control means controlling the operation of the power drive means and adapted to be set to vary the speed of rotation of the shaft, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively-associated with the control setting means and with the control means and operative by governor action to maintain the speed of rotation of the shaft within predetermined limits with respect to an idling speed, and operative by governor action to limit the maximum speed of rotation of the shaft, the governor means including centrifugally actuated governor weights, externally accessible simplified means for adjusting the maximum speed at which the governor action takes place, and externally accessible simplified means for adjusting the idling speed governor action of the apparatus.

Improved variable control setting means are provided, by which very accurate initial adjustments of the control setting means may be made.

In the form of the improved governor apparatus adapted for use in connection with an engine for providing variable torque for a power shovel and the like, means are provided whereby two successive intermediate governor actions take place at predetermined speeds after each of which a. different change in the torque of the engine is obtained.

The improved apparatus furthermore includes improved means for stopping the engine associated with parts of the improved adjustable means for setting the idling speed-of the engine.

The improved governor apparatus is preferably included in and/ or combined with a compression ignition internal combustion engine as is hereinafter set forth in greater detail, and the engine and apparatus also may include further novel improvements illustrated in the drawings and/or as hereinafter set forth.

Embodiments of the improved governor apparatus are illustrated in the accompanying drawings forming part hereof, in which Figure 1 is a side elevation view of a compression ignition internal combustion engine having a fuel pump equipped with one embodiment of the improved governor apparatus of the present invention and being adapted for use as the motive power of a vehicle;

Fig. 2, an enlarged transverse sectional view of the improved governor apparatus, as on line 2-2, Fig. 1, distant parts of the engine and fuel pump, being removed;

Fig. 3, a fragmentary side elevation with portions broken away of the improved governor apparatus and portions of the fuel pump, distant parts of the engine being removed;

Fig. 4, an enlarged fragmentary longitudinal sectional view of the improved governor apparatus and portions of the fuel pump, distant parts of the engine being removed, as on line 44, Fig. 2; a

Fig. 5, a fragmentary elevation with portions broken away of the improved governor apparatus, illustrating the side thereof opposite to the side shown in Fig. 3, and showing the details of the improved stop means and parts of the variable adjusting means for the governor apparatus; and

Fig. 6, a; view similar to Fig. 4 illustrating another embodiment of the improved governor apparatusadapted for automatically providing a variable torque control for an engine used as a power source for a power shovel or the like.

Similar numerals refer to similar parts throughout the several views.

A compression ignition internal combustion engine equipped with one embodiment of the present improved governor apparatus is indicated generally at It) in Figs. 1 to 5, inclusive, and as illustrated is a six cylinder, four strokecycle, single action, high speed, compression ignition internal combustion engine, in which the air'for combustion is obtained normally directly from the atmosphere, and in which separate quantities or charges of the preferred liquid hydrocarbon fuel, such as Diesel oil, are successively injected by-operation of a fuel pump indicated generally by H, into the combustion chambers of the engine at successive timed intervals, one charge being injected into the combustion chambers of each cylinder during each four stroke cycle of the piston operatively mounted in the cylinder.

The fuel pump II is operatively mounted on one side of the engine as shown in Fig. 1, and as illustrated is of usual construction and arrangement and isa Bosch fuel injection pump, made by Robert Bosch, A. G., Stuttgart, Germany, and includes a shaft 12, driven by an operative connection with gearing contained in a gear housing l3 of the engine, the gears in the gear housing being driven by the engine crank shaft. The gears and crank shaft are not shown, and may be of a usual construction and arrangement.

The fuel pump l I includes a casing H in which plunger pistons, not shown, are operatively mounted, each in a pump cylinder, not shown, formed in the casing I4, one pump plunger piston and cylinder being provided for each cylinder of the engine.

The plunger pistons are actuated in a usual manner by cams on a cam shaft portion, not shown, of the shaft l2, the cam shaft portion being located within a cam shaft chamber of the casing H.

Each pump cylinder communicates with a discharge outlet |5 which communicatingly connects with one end of a tube I6, the other end of which communicatinglyconnects with a pintle nozzle discharging into the combustion chambers of one of the engine cylinders.

The liquid fuel is supplied to the pump H through a main supply tube H in which an oil cleaner l8 may be interposed ahead of the fuel pump H.

The fuel pump is provided with the present improved governor apparatus indicated generally by l9, and the fuel pump also includes valve or variable metering means for each fuel pump cylinder controlling the quantity of liquid fuel admitted to each pump cylinder from the main supply tube and thus controlling the quantity of fuel in each charge pumped out of each pump cylinder into its associated engine cylinder combustion chambers on the pressure stroke of the piston of the pump cylinder.

The fuel pump l I furthermoreincludes a valve setting or throttle rod 20 which is operatively associated with each of the valve means for each of the pump cylinders and which is arranged for reciprocation in normally horizontal opposite directions in the casing H of the fuel pump II.

The rod 20, when displaced to its extreme po-' sition in the direction of the arrow S, in Figs. 3 and 4 actuates the valve means so as to shut off the flow of liquid fuel into the pump cylinders, and thus stops the engine. At the position of the rod 20 and associated parts as illustrated in full lines in Figs. 3 and 4, the pump valve means are set to a position for permitting a flow of fuel into the pump cylinders at such rate as to cause the engine It) to operate at a desired idling speed.

Displacement of the rod 20 in the direction of the arrow F actuates the pump valve means to increase the rate of flow of liquid fuel into the pump cylinders, the greater the displacement of the rod 20 in the direction of the arrow F, the greater the rate of flow of liquid fuel into the pump cylinders.

Accordingly the valve means of the pump cyling the speed of operation of the engine, and the rod 22 may be termed a control means actuating member which is movable between two extreme positions, one of which is such that the control means are actuated to stop the engine or apparatus controlled by the control or valve means, and the other of which is such that the control means are actuated so as to run the engine at full speed. and intermediate positions of which include a setting which provides an idling speed for the engine, and provides for varying speeds thereof between the idling speed and the full speed.

The governor apparatus i9 preferably includes a casing indicated generally by 2| and which comprises walls forming a governor chamber 22, and which in the illustrated embodiment consists of two casing sections 22 and 22' secured to each other, and the casing section 22 being secured to the pump casing l4.

The governor casing section 22' includes an end wall 24 which abuts against the adjacent end wall 25 of the pump casing l4, and the governor drive end 29 of the pump shaft |2 extends through suitable apertures formed in the pump casing wall 25 and the governor casing wall 24, and preferably anti-friction bearing means indicated generally by 21 journal the shaft in the governor casing wall '24, and-the governor drive 7 end 26 of the pump shaft l2 terminates within the governor chamber 22.

A governor drive gear 22 is secured upon the govemor drive end 22 of the pump shaft l2 within the governor chamber 22, and also within the governor chamber, a governor shaft 29 is journal mounted at opposite ends as by means of antifriction bearing means indicated generally by 22 and 2|,respectively, which are themselves re-. spectively mounted in the governor casing end wall 24, and on the opposite governor casing end wall 22.

The longitudinal axis of rotation of the governor shaft 29 is preferably parallel with the longitudinal axis of rotation of the pump shaft l2 and the governor shaft has secured thereon a driven pinion 22 which is located adjacent the anti-friction bearing means 20 and which is meshed with the governor drive gear 22, whereby rotation of the pump shaft l2 driven as aforesaid frcm the crank shaft of the engine, serves to rotate the governor shaft 22'. I

The governor shaft 29 has secured thereon, in the illustrated embodiment adjacent the driven pinion 22, a spider 24 having sets of arms 29 and '29 respectively extending from diametrically opposite sides of the shaft 29, and governor weights 29 and 29' are pivotally mounted intermediate their ends respectively on the opposite sets of spider arms 25 and 25', as by means of spider pins 21 and 21, the longitudinal axes of which are parallel, and which are spaced at equal distances from the longitudinal axis of the governor shaft 29, and lie in a plane normal to the longitudinal axis of the shaft 29.

The governor weights 29 and 29? are of a desired shape, and are substantially identical with each other, and have their centers of gravity located at equal distances from the longitudinal axes of the pins 91 and 31"beyond the outer extremities of the sets of spider arms 22 and 25'. Thegovernor weights 26 and 29' include respectively sleeve actuating tongues 22 and 22' which extend toward the governor shaft 29, the

inders may be termed control means determinspider pins 21 and 21 and the governor shaft 22.

The governor weights 22 and 22 also include at their inner extremities stop tongues 22 and 22' which abut against opposite stop faces on the spider hub 42 and limit the outward movement of the weights 22 and 22' under the action of the centrifugal forces set up therein by rotation of the shaft 22.

A sleeve 4| is slidably mounted on the governor shaft 22 between the spider 24 and the outer bearing means 2| for the governor shaft 22, and

the end face 42 of the sleeve 4| adjacent the tongues 22 and 22' of the governor weights 22 and 22' is abuttable by the outer extremities of the tongues 22 and 22', and the sleeve 4| is longitudinally movable on the shaft 22.

Intermediate its ends, the sleeve 4| has rotatably mounted thereon a ring 42, the mounting of the ring 42 on the sleeve 4| being preferably as iil-lusgated by means of an anti-friction bear- The governor apparatus 9 furthermore includes a yoke lever pivoting eccentric shaft 42 which is journalled at its ends in the opposite side walls 42 and 41 of the governor casing section 22, and which is located at one side of, and

as illustrated, normally below the governor shaft 29, the longitudinal axis of the eccentric shaft 42 extending at right angles to the direction-of the longitudinal axis of the governor shaft 22.

A yoke lever 42 is pivotally mounted at one end 49 on the eccentric shaft 42, and the yoke lever end 42 as illustrated is the lower end of the yoke lever 42.

The yoke lever 42 has formed therein a central 7 opening 22, and the governor shaft 29, the sleeve 4|, and the ring 42 rotatably mounted on the sleeve 4| as aforesaid, extend through and/or are located within the central opening 22 of the yoke lever 42.

The yoke lever 42 includes side members 2| and ii comprising in part the boundary members for the opening 52 and the yoke side members II and II are located on opposite sides of the shaft 29, the sleeve 4| and the ring 42.

The ring 42 has formed in its outer peripheral surface an outwardly opening annular groove 22 and pins 22 and 22' have their outer ends respectively secured in the yokev side members II and Ii and have their inner ends extending into the ring groove 22.

' At the upper corner of the yoke lever 42 opposite the outer end of the rod 22, a connector ear I4 is provided and a longitudinally adjustable link means is pivotally connected at its outer end with the ear 24, as by pin means 22, and the link means 29 is pivotally connected at its inner end with the outer extremity of the rod 22 as by pin means 21.

Preferably a, compression spring 12 is interposed betweenthe upper end of the yoke lever 42, and an externally threaded adjustable screw plug 1| screwed in an internally threaded bore formed in the governor casing wall 22, the upper end of the yoke lever 42 and the plug 1| preferably having opp itely opening sockets formed therein into which the opposite ends of the comtongues 22 and 22' being located between the For the 111190868 of the present improvements,

the anti-friction bearing means 3| for the governor shaft 29 is carried in externally accessible means indicated generally by 12 for adjusting and determining the maximum speed at which governor action takes place, as aforesaid.

The maximum speed governor action adjuste ing means 12 includes a tubular member 19, which is preferably externally cylindric in its central portions and whose externally cylindric central portions fit in a cylindric bore formed in the governor casing end wall 32, the ends of the tubular member I3 extending beyond opposite sides of the casing end wall 32, and the inner end of the tubular member 13 being provided within the governor chamber 22 with an inwardly extending annular flange 14.

The tubular member 13 on the outside of the casing wall 32 is provided with an'outwarclly extending annular flange 15, and initial clearance shims 16 are interposed between the flange 18 and the wall 32.

The outer end ll of the tubular member I3 extends outwardly beyond the flange IS.

A bearing and adjusting means mounting cap 18 is mounted on the outer end 11 of the tubular member I3.

The cap 78 is provided with an internal socket 80 formed to seat at its outer end the outer raceway member 3| a of the ball anti-friction bearing means 3| illustrated, the inner raceway member 3|b of which mounts the outer end of the'governor shaft 29, as aforesaid.

The cap socket 80 has rotatably mounted therein in rotary abutment with the inner side of the outer raceway member 3|a of the ball anti-friction bearing means iii, a ring 86 which is provided with external worm wheel threads 82 and the bore 83 of which is substantially larger in diameter than the diameter of the shaft 29 which extends therethrough.

The socket 88 includes an enlarged inner end portion or counterbore 84 which fits on the outer end ll of the tubular member 13, and the outer extremity of the tubular member 13 terminates intermediate the ends of the enlarged portion 84 of the cap 18, and a spring seat member 88 is located in the counterbore 84 between the ring 8| and the outer extremity of the tubular mem-' ber 13.

The spring seat member 88 includes a central sleeve hub 81 through the bore of which the shaft 29 passes and which extends into the bore 88 of the ring 8|, the hub 81 and the ring 8| being screw connected with one another by internal threads 88| in the bore 83 of the ring, and external threads 88-2 on the hub 81.

For preventing rotary movement of the spring scat member 88, a tongue and notch connection thereof with the outer end ll of the tubular member I3 is provided, as illustrated by tongues -88| extending from the seat member 88 into the openings of notches formed in the outer end ll of the tubular member 13.

The cap 18 has journal mounted therein a worm screw 89 having a screw head 90 located externally of the cap 18, and the worm screw 89 is meshed with the worm threads 82 formed externally in the ring 8 I, and accordingly rotation of the worm screw 89 serves to turn the ring 8 I, and the spring seat 86 screw connected with the ring 8| and prevented from rotation by its end tongue and notch connection with the tubular member 13, is caused to be displaced with respect to the tubular member I3.

A reacting ring 9| extends through the opening of the annular flange ll of the tubular member 19, and the reacting ring 9| is provided within the bore of the tubular member I3 with an outwardly extending annular flange 92 normally abutting against the inwardly extending annular flange l4 0! the tubular member 13.

The reacting ring 9| is provided on its end within the governor chamber 22 with an inwardly extending annular flange 93 and a compression spring 94 is interposed between the spring seat member 86 and the inwardly extending annular flange 93 of the reacting ring 9|.

The cap 18 as illustrated is provided at its inner end with a flange 95 and a gasket 98 is preferably interposed between the flange 95 and the flange 15 of the tubular member 73, and screws 91 preferably secure and seal the flange 95 to the flange 15 .whereby the maximum speed governor action adjusting means 12 above described including the tubular member I3, the cap E8 and the parts operatively mounted therein, may be preassembled as a unit and may be easily inserted upon or removed from the outer end of the shaft 29.

Cap screws 98 are provided as shown for securing the unitary maximum speed governor action adjusting means 12 to the wall 32.

The eccentric shaft 45 includes an eccentric portion 45a on which the yoke lever end 49 is pivotally or rotatably mounted as aforesaid, and the eccentric shaft, furthermore includes axially alined end journal portions 451) and 450 which are rotatably mounted respectively in the governor casing side walls 48 and 41, and the journal portion 95b of the eccentric shaft 45 extends beyond the outer side of the casing side wall 41 and has secured thereon externally of the governor casing 2|, a control setting lever 68-2, the

rotate about the axis 99 of the journal portions 45b and 450 as indicated by the dot-dash line in Fig. 2, and at the intersection of dot-dash lines in Fig. 4, and the center axis of the eccentric portion 45a of the eccentric shaft 45 is indicated at I08 in Fig. 4, by intersecting dot-dash lines, one of which |0| passes through the center axis 99 of the journal portions 45b and 450, and the dot-dash line |0| is thus the eccentric lever or crank arm of the eccentric shaft 45, which swings about the center axis 99. I

As is more fully set forth in the following description of the operation of the improved governor apparatus l9, swinging of the eccentric lever arm ||I| in the direction of the arrow F, Fig. 4, serves to increase the speed of the engine l0, and swinging of the eccentric lever arm |8| in the direction of the arrow S, Fig. 4, serves to decrease the speed of the engine l0. The parts of the governor apparatus |9 as illustrated in the drawings are in their several relative positions by which idling speed of the engine is obtained.

As best shown in Fig. 4, the maximum speed governor action adjusting means 12 is provided with an initial clearance by means of the shims I6, whereby the outer face of the flange'93 is normally spaced a slight distance from the antifriction bearing 44, and the tendency of the governor weights 36 and 36' to move the sleeve 4| and the yoke lever 48 towards the casing wall 32 is opposed by the spring 19, which is so adjusted thataslightincreaseinthe'speedoftheengine beyond the idling speed will cause the weights and 00' to move outwardly and will slightly advance the yoke lever, 40 pivoting about the center axis I00 of the eccentric portion 45a of the eccentric shaft 45 towards the flange 00, and will thus move the rod 20 in the direction of the arrow B and will slightly decrease the rate of flow of fuel and slow down the engine speed to the idling speed; and on the other hand a slight decreasein the speed of the engine will permitried thereby on the bearing 44 by virtue of the forces applied to the sleeve, by the tongues 00 and 08' of the weights "and due to the varying centrifugal forces acting upon the weights '30 and 30' and tending to throw the same outwardiy about the pins 31 and II.

Accordingly during normal operation of the engine, swinging the control setting lever 002 in the usual manner by stepping upon the accelerator pedal or swinging the accelerator lever causes the eccentric shaft lever arm III to swing about the center axis 50, thus pivoting the yoke lever 40 about the pins 50 and 50' so that when the eccentric shaft lever arm III is swung in the direction of the arrow F, the rod will be moved in the direction of the arrow 1'' so as to increase spring 04, and permitting the extension of thespring 94 to its position to maintain the maxithe rate of flow of fuel and the speed of the engine, and conversely swinging of the eccentric shaft lever arm IOI inthe direction of the'srrow S will move the rod 20 in the direction of the arrow S and decrease the rate and the speed of the engine."

. Excepting at the idling speed as aforesaid, as long as the speed of the engine, and consequently the speed of the governor shaft does not exceed a predetermined maximum, established by the loading of the spring 04, no governor action whatever takes place.

If, however, by accident, or during a release of the engine clutch, or otherwise, regardless of the setting of the control setting lever 00-2 and the eccentric shaft 45, the speed of the engine and consequently the speed of the governor shaft 20 exceeds the set maximum speed, then the force.

tending to move the sleeve 4I, and the anti-friction bearing 44 and the ring exceeds the opposing force of the spring 04, compression of the I spring 04 takes place, and the yoke lever 40. pivots mum governed speed.

Loading of the spring 04 to establish the maximum speed of the engine iseffected by turning.

the external screw head 00 of the worm screw 00.

Preferably the eccentric shaft is mounted in the casing side walls 40 and 41, by providing in each of the opposite side walls 40 and 41 aligned of flow of fuelbores I02 and I05, respectively, the diameters of the bores I02 and I 03 being large enough to permit the endwise insertion and removal there.- through of the eccentric shaft 45.

The bore I02 of the wall 40 has removably secured therein a bearing and bracket plug I04 which has a bearingbore iournalling the eccentric shaft Journal portion 45c; and the bore I02 in.the wall 41 has removably secured therein a bearing plug I05 which has a bearing bore there- 11; 3011 the eccentric shaft Journal porti The control setting lever 09-2 is preferably ad-' Justably secured on the external end of the shaft portion 45b as best shown in Figs. 3 and 4 by worm screw and worm wheel means indicated generally by I00 and which include a worm wheel I01 secured on the shaft portion 45b and the worm wheel III is engirdled-by a split rlng hub I00 provided on the lever 00-2 and a worm screw III is iournalled and extends through opposite split portions III and III of the hub and the threads of the screw I05 are meshed with the threads of the worm wheel I01, whereby rotation of the worm screw enables adjustment of the position of the arm -2, to the proper position with respect to the mechanism of the apparatus within the'casing 2I and with respect to the external connections to the accelerator pedal or like control for the en ine.

The outer screw end of the worm screw I00 preferably is provided with a lock or clamping nut II2.

A maximum speed stop pin IIO.is secured on a plate II4 interposed between the hub I00 and the plug I05 and secured to the plug I05-and the hub I00 has a maximum speed stop tongue II5 extending therefrom and adapted to stop abut against the pin II3.

Within the borel00the end of the plug I05 is notched to form a stop face IIG adapted to be abutted by a pin I I1 extending from the opposite end of the eccentric portion 45a to limit motion of the eccentric in the direction causing a shut! ting off of the fuel supply.

The plug and bracket I04 as best shown in Fig. 5 is secured to the outer side of the casing wall 40 and the eccentric shaft portion 45c extends beyond the outer face of the plug and bracket I04 and has associated therewith preferably adjustable idling speed setting and engine stop means indicated generally by IIO which prevents rotation of the shaft 45 in the fuel shutting of! direction normally beyond a position permitting governor controlled,

idling speed operation of the engine.

The idling speed setting and engine stop means III preferably include a single tooth ratchet split ring I I0 engirdling a worm wheel I20 which is mined on the shaft end portion 450, and a worm screw I2I' extends through aligned. bores in op-- posite split ends I22 and I23 of the ring 9, and the threads of the screw I2I are meshed with the threads of the worm wheel I 20 whereby minute adjustment of the position of the tooth I 24 of the ratchet ring 0 with respect to the shaft 45 and the other parts of the apparatus within the casing H is attained. I i

A hook pawl I25 is pivotally mounted on the bracket I04 and the hook pawl I 25 includes a stop hook end I26 which is urged towards the shaft 450 by spring means I21 and provides a releasable idling speed stop adapted to impinge the ratchet tooth I24 and prevent further rotation of the coitigentric shaft 45 beyond the idling speed setting reof.

For permitting stopping of the engine, the pawl I25 includes a release arm I29 which as illustrated is connected as by a wire I29 with the dash board or the like of the vehicle or other apparatus with which the governor means I9 is associated, and by pulling the wire I29, the pawl stop hook end I23 is released for engagement from the tooth I24 permitting further rotation of the shaft 45 in. the

fuel shutting off direction so as to stop the engine.

In Fig. 6a modified embodiment I3 of the improved governor apparatus is illustrated, and the governor apparatus I9 is adapted for a variable torque control of a Diesel engine, such as the engine I0 when used as a power supply for a power shovel.

The parts of the governor apparatus I9, as illustrated are identical with the parts of the apparatus I9 heretofore described, with the'following exceptions.

In the governor apparatus l9, the spring 94 is not utilized and there is interposed between the reaction member 9| and the spring seat member 86 an intermediate double spring seat and stop member I30 including a sleeve portion I3I from which extends an annular flange I32 opposite the reacting member flange 93. I

The member I30 also includes an outwardly extending annular stop and spring seat flange I33 which is opposite the spring seat member 86 and which normally abuts against a shoulder I34 formed in the end of the tubular member 13 ad jacent the shoulder flange 14.

A compression spring I35 is interposed between and reacts against the adjustable spring seat member 86 and the flange I33 of the intermediate member I30, and another compression spring I36 is interposed between the reacting member flange 93 and the flange I32 of the intermediate mem- 'ber I30.

The resistance or loading of the springs I 35 and I36 are different from each other, the spring I33 having the least initial load, and the rate of deflection however of the spring I35 is greater than the rate of deflection of the spring I38.

Accordingly when the speed of the engine, as in a power shovel, reaches for example 900 R. P. M., the force tending to move the sleeve 4| and the yoke lever 48 becomes such as to pivot the yoke lever 48 about the eccentric portion 45:: of the shaft 45 toward the casing wall 32 compressing the spring I36 and cutting off the fuel supply of the engine so as to reduce the torque of the same while the engine speed is further increased.

After the engine speed has increased to 1300 R. P. M. for example, the reacting member 9I abuts against the intermediate member I30 and the force tending to move the sleeve 4I may then have attained such magnitude as to rapidly compress the spring I35 and rapidly shut off the supply of fuel to the engine until if desired the entire fuel supply is shut oif.

In the practical operation of a power shovel for example, the normal shovel speed may be 1300 'R. P. M., and accordingly when the shovel engine tion of the rotary shaft driven thereby, control setting means operatively associated with the applying a force in the opposite direction against the lever, the lever adjacent one end thereof having an operative connection with the variable control means, and the control setting means including a crank pivotally mounting the lever adjacent the other end thereof, and the resilient means being loaded so as to prevent movement of the lever by the action of the centrifugally induced force of the governor means during a normal speed range of the rotary shaft.

2. Governor controlled apparatus including a rotary shaft, power drive means for the shaft, variable control means controlling the operation of the power drive means and the speed of rotation of the rotary shaft driven thereby, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means and with the control means and with the control setting means, the governor means including a lever operating the variable control means and operated by the control setting means, centrifugally operating means pivotally and slidably associated with the lever intermediate its ends and connected for rotation by the shaft and adapted to apply a force in one direction against the lever, and adjustable resilient means applying a force in the opposite direction against the lever, the lever adjacent one end thereof having an operative connection with the variable control means, and the control setting means including a crank pivotally mounting the lever adjacent the other end thereof, and the resilient means being loaded so as to prevent movement of the lever by the action of the centrifugally induced force of the governor means during a normal speed range of the rotary shaft.

3. Governor controlled apparatus including a rotary shaft, power drive means for the shaft, variable control means controlling the operation of the power drive means and the speed of rotation of the rotary shaft driven thereby, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means and with the control means and with the control setting means, the governor means including a lever operating the variable control means and operated by the control setting means, centrifugally operating means pivotally and slidably associated with the lever intermediate its ends and connected for rotation by the shaft and adapted to apply a force in one direction against the lever, and resilient means including a spring pressed reacting member located at the side of the lever opposite the direction of the centrifugally applied force, and the spring pressed reacting member being adapted to be abutted by the lever and resist movement thereof by the action of the centrifugally applied force, the lever adjacent one end thereof having an operative connection with the variable rotary shaft, power drive means for the shaft,

variable control means controlling the operation of the power drive means and the speed of rotation of the rotary shaft driven thereby, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means and with the control means and with the control setting means, the governor means including a lever operating the variable control means andoperated by the control setting means, centrifugally operating means pivotally and slidably associated with the lever intermediate its ends and connected'for rotation by the shaft and adapted to apply a force in one direction against the lever, and resilient means including an adjustable spring pressed reacting member located at the side of the lever opposite the direction of the centrifugally applied force, and the spring pressed reacting member being adapted to be abutted by the lever and resist movement thereof by the action of the centrifugally applied force, the lever adjacent one end thereof having an operative connection with the variable control means, and the control setting means including a crank pivotally mounting the lever adjacent the other endthereof, and the resilient means being loaded so as to prevent movement of the lever by the action of the centrifugally induced force of the governor means during a normal speed range of the rotary shaft.

5. Governor controlled apparatus including a rotary shaft, power drive means for the shaft, variable control means controlling the operation of the power drive means and the speed of rotation of the rotary shaft driven thereby, control setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means andwith the control means and with the control setting means, the governor means including a lever operating the variable control means and operated by the control setting means, centrifugaliy operating means pivotally and slidably associated with the lever intermediate its ends and connected for rotation by the shaft and adapted to apply a force in one direction against the lever, and resilient means including a spring pressed reacting member located at the side of the lever opposite the direction of the centrifugally ap l ed force, and the spring pressed. reacting member being adapted to be abutted by the lever and resist movement thereof by the action of the centrifugally applied force, and resilient means adapted to apply a second force upon the lever in the opposite direction to the centrifugally applied foran'the lever adjacent one end thereof having an operative connection with the variable control means, and the control setting means including a crank pivotally mounting the lever adjacent the other end thereof, and the resilient means being loaded o as to prevent movement of the lever by the action of the centrifugally induced force of the governor means during a normal speed range of the rotary shaft.

, 6. In governor apparatus and the like, adjustable resilient reacting means including a longitudinally extending mounting member having a stop flange at one end, a reacting member mounted for longitudinal movement with respect to the mounting member, the reacting member hav-' ing a flange normally abutting against the mounting member stop flange, a ,spring seat member, means adiustably mounting the spring seat member on the mounting member with the reacting member located between the mounting member stop flange and the spring seat member,

a compression spring interposed between the 'reacting member and the spring seat member, thespring seat member mounting means including a rotary member operatively associated with the spring seat member whereby rotation of the rotary member moves the spring seat member longitudinally for varying the loading of the spring, the rotary member having worm wheel I threads thereon and a worm screw operatively associated with the worm wheel threads for turning the rotary member.

7. In governor apparatus and the like, unitary adjustable resilient reacting means including a longitudinally extending tubular mounting member having a stop flange at one end, 'a reacting member mounted for longitudinal movement with respect to the tubular member, the reacting member having a flange within the bore of the tubular member and normally abutting against the tubular member stop flange, a cap secured on the other end of the tubular member, the cap having a longitudinally extending socket formed therein and comprising a longitudinal extension of the bore of the tubular member, a spring seat member located "within the socket, a compression spring interposed between the reacting member and the spring seat member, a rotary member rotatably mounted in the socket and operatively associated with the spring seat member whereby rotation of the rotary member moves the spring seat member longitudinally for varying the loading of the spring, the rotary member having worm wheel threads thereon, a worm screw rotatably mounted in the cap and operatively associated with the worm wheel threads, and the worm screw having a head located externally of the cap whereby the worm screw head may be turned from without the cap and the rotary member is turned thereby to adjust the position of the spring seat member.

8. In governor apparatus and the like, a casing, governor controlled valve setting means operatively mounted within the casing, means for varying the setting of the valve setting means including a shaft operatively associated with the valve setting means within the casing, the shaft extending externally of the casing, a control lever, and means adiustably mounting the control lever on the shaft outside of the casing, the means adjustably mounting the control lever on the shaft including interacting members on the lever and the shaft adapted for operation to vary and set the angular position of the lever with respect to an element of the shaft.

9. In governor apparatus and the like, a casing, governor controlled valve setting means operatively mounted within the casing, a shaft operatively associated with the valve setting means within the casing, the shaft extending externally of the casing, the shaft being adapted for manual rotation outside of the casing for varying the setting of the valve setting means within the casing, means outside of the casing for releasably stopping rotation of the shaft in one direction beyond a position establishing an in termediate governor controlled setting of the valve setting means within the casing.

10. In governor apparatus and the like, a casing, governor controlled valvesetting means operatively mounted within the casing, a shaft operatively associated with the valve setting means within the casing, the shaft extending externally of the casing, the shaft being adapted for manual rotation outside of the casing ior varying the setting of the valve setting means within the casing, means outside of the easing for releasably stopping rotation of the shaft in one direction beyond a position establishing an intermediate governor controlled setting of the valve setting means withinthe casing, and means for manually releasing the releasable stop means from stopping relationship with the shaft.

11. In governor apparatus and the like, a casing, governor controlled valve setting means operatively mounted within the casing; a shaft operatively associated with the valve setting means within the casing, the shaft extending externally of the casing, the shaft being adapted for manual rotation outside of the casing for varying the setting of the valve setting means within the casing, means outside of the casing for releasably stopping rotation of the shaft in one direction beyond a position establishing an intermediate governor controlled setting of the valve setting means within the casing, the releasable stop means including a ratchet secured on the shaft, the ratchet having a single stop tooth, and a pawl associated with the ratchet and normally maintained in position for engaging the ratchet stop tooth.

12. In governor apparatus and the like, a casing, governor controlled valve setting means operatively mounted within the casing, a shaft operatively associated with the valve setting means within thecasing, the shaft extending externally of the casing, the shaft being adapted for manual rotation outside of the casing for varying the setting of the valve setting means within the casing, means outside of the casing for releasably stopping rotation of the shaft in one direction beyond a position establishing an intermediate governor controlled setting of the valve setting means within the casing, the releasable stop means including a ratchet secured on the shaft, the ratchet having a single stop tooth, and

a pawl associated with the ratchet and normally setting means operatively associated with the control means for varying the setting of the same, and governor means operatively associated with the power drive means and with the control means and with the control setting means, the governor means including a 'movably mounted lever operating the variable control means and operated by the control setting means, centrifugally operating means associated with the lever and with the rotary shaft and adapted to apply a force in one direction against the lever, and resilient reacting means operative to opposed movement of the lever by the action of the centrifugally applied force, the resilient reacting means including a plurality of springs arranged to deflect successively under the action of the centrifugally applied force, each spring having a different rate of deflection.

14. In governor apparatus and the like, resilient reacting means including a longitudinally extending mounting member having a stop flange at one end, a reacting member mounted for longitudinal movement with respect to the mounting member, the reacting member having a flange normally abutting against the mounting member stop flange, a first spring seat member mounted on the mounting member with the reacting member located between the mounting member stop flange and the first spring seat member, an intermediate spring seat member located between the reacting member and the first spring seat member, a first compression spring interposed between the first spring seat member and the intermediate spring seat member and a second compression spring interposed between the intermediate spring seat member and the reacting member.

15. In governor apparatus and the like, resilient reacting means including a longitudinally extending mounting member having a stop flange at one end, a reacting member mounted for longitudinal movement with respect to the mounting member, the reacting member having a flange normally abutting against the mounting member stop flange, a first spring seat member mounted on the mounting member with the reacting member located between the mounting member stop flange and the first spring seat member, an intermediate spring seat member located between the reacting member and the first spring seat member, a first compression spring interposed between the firstspring seat member and the intermediate spring seat member and a second compression spring interposed between the intermediate spring seat member and the reacting member, the springs having diiferent rates of deflection.

WILLIAM F. ENGEL. GEORGE W. LA SALLE. OTIS D. TREJBER. 

